WO2009106623A1 - Joint fileté avec anneau d’étanchéité élastique amélioré - Google Patents

Joint fileté avec anneau d’étanchéité élastique amélioré Download PDF

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Publication number
WO2009106623A1
WO2009106623A1 PCT/EP2009/052388 EP2009052388W WO2009106623A1 WO 2009106623 A1 WO2009106623 A1 WO 2009106623A1 EP 2009052388 W EP2009052388 W EP 2009052388W WO 2009106623 A1 WO2009106623 A1 WO 2009106623A1
Authority
WO
WIPO (PCT)
Prior art keywords
seal ring
box
threaded joint
joint according
ring
Prior art date
Application number
PCT/EP2009/052388
Other languages
English (en)
Inventor
Nestor J. Santi
Gaston Mazzaferro
Alfredo Francisco Quiroga
Original Assignee
Tenaris Connections Ag
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Tenaris Connections Ag filed Critical Tenaris Connections Ag
Priority to JP2010548127A priority Critical patent/JP2011514490A/ja
Priority to MX2010009517A priority patent/MX2010009517A/es
Priority to CA2716586A priority patent/CA2716586C/fr
Priority to BRPI0907993-9A priority patent/BRPI0907993B1/pt
Priority to US12/920,085 priority patent/US8262140B2/en
Priority to CN200980106481.1A priority patent/CN102027186B/zh
Priority to RU2010139822/03A priority patent/RU2472916C2/ru
Publication of WO2009106623A1 publication Critical patent/WO2009106623A1/fr
Priority to NO20101182A priority patent/NO337939B1/no

Links

Classifications

    • E—FIXED CONSTRUCTIONS
    • E21—EARTH DRILLING; MINING
    • E21B—EARTH DRILLING, e.g. DEEP DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B17/00—Drilling rods or pipes; Flexible drill strings; Kellies; Drill collars; Sucker rods; Cables; Casings; Tubings
    • E21B17/02—Couplings; joints
    • E21B17/04—Couplings; joints between rod or the like and bit or between rod and rod or the like
    • E21B17/042—Threaded
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L15/00—Screw-threaded joints; Forms of screw-threads for such joints
    • F16L15/001—Screw-threaded joints; Forms of screw-threads for such joints with conical threads
    • F16L15/003—Screw-threaded joints; Forms of screw-threads for such joints with conical threads with sealing rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L15/00—Screw-threaded joints; Forms of screw-threads for such joints
    • F16L15/04—Screw-threaded joints; Forms of screw-threads for such joints with additional sealings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B2200/00—Constructional details of connections not covered for in other groups of this subclass
    • F16B2200/60—Coupler sealing means

Definitions

  • the present invention relates to threaded joints, in particular for connecting tubes of predefined length to make strings used in the hydrocarbon industry especially for use in the field of OCTG (Oil Country Tubular Goods) and in line pipes in offshore applications.
  • OCTG Olet Country Tubular Goods
  • the joint seals resist penetration of the external fluids, or at least do not allow continuous exchange of the fluids already penetrated with the surrounding fluids, in order to reduce corrosion rate of the joint.
  • various solutions have been suggested, one of which consists of inserting a seal ring made of polymeric material, e.g. an O-ring, at the extremity of the joint near the threaded portion.
  • seals are usually pre-mounted onto the box, when making up the box the seal is dragged together with the box over the pin's threads. Due to the diametrical interferences needed between pin, box and seal dimensions for the seals to work properly, along with the geometric parameters of the connection such as thread profile, pitch, taper angle, stab angle, etc, the seals are inevitably forced to crawl over the pin's threads, causing damage to the lower surfaces of the seals or permanent deformations to the seal which would jeopardize the sealing efficiency during operation.
  • Seal rings having more complicated shape have also been proposed, e.g. rings with an "H" or "U”-shaped cross section to increase efficiency and prevent sea water from penetrating into the gaps of the joint.
  • seal rings are subject to such stresses and adverse environmental conditions, both during the initial make-up operation and during operational life, that their efficiency is much reduced after some time.
  • pre-mounting on the pin would be less harmful for the seal ring, some field applications require seal rings of simpler shape which must be pre-mounted onto the box.
  • US6550822 discloses a threaded joint including a water exclusion seal which is a pressure energized elastomeric seal positioned in a groove near each end of the joint to make a radial seal between the unthreaded area at each end of the joint and the unthreaded cylindrical area adjacent each end of the tubular section.
  • the shape of the ring section does not facilitate its dragging over the thread during make up. Because of this shape, the sharp corners hit the thread crests and are prone to get stuck in the thread. In case of joint break-out it becomes even more likely to damage the seal ring.
  • the principal object of the present invention is to provide a joint having two innovative seal rings ensuring both a simple and reliable initial make-up and a high sealing efficiency during operation, particularly resistant to infiltrations of corrosive external fluids.
  • a threaded joint that, according to claim 1 , comprises a male threaded pipe, defined as the pin, a female threaded pipe, defined as the box, the pin being configured to be made up in the box, pin and box defining a common longitudinal axis, a first seal ring and a second seal ring interposed between the pin and the box, and located in a portion of the surface of the box between the end of a threaded portion and the nose of the box, and being in tight sealing contact by means of respective radially external surfaces on one side with an internal surface of the box and by means of respective radially internal surfaces with an external surface of the pin, the internal surface of the box being provided with a first recess made in proximity of the nose of the box for housing the first seal ring and with a second recess made in its thickness for housing the second seal ring placed between the first recess and the threaded portion of the box.
  • the joint according to the invention has two seal rings of novel design which ensure optimal sealability under particularly adverse operative conditions: the second or internal seal ring protects the threaded portions of the joint; the first or external seal ring protects in turn the second seal ring further improving the protection of the joint.
  • the solution according to the invention is more reliable in cases where no spare O-rings are available. Contrary to joints having seals of the prior art, like O-rings with circular cross section or similar, the joint according to the invention does not cause damage to the seal rings during break-out. This has the advantage that the same seal rings can be used for a successive make up operation.
  • the first seal ring placed most externally to the joint has a cross section shape particularly suitable to be pushed like a wedge by the external fluid pressure deep into the space between the external lip of the box and the corresponding external surface of the pin, thereby improving the sealing capacity of the ring and consequently of the joint.
  • the fact of making the housing for the first seal ring in the internal surface of the box frustoconical in the portion coming into contact with the first ring, with its taper toward the inside of the box further enhances contact of the first seal ring with the metal surfaces, improving sealing capacity. It also ensures that, starting from a limit pressure, the seal ring fully fits into the annular space between the lip of the box and the facing pin external wall.
  • a further advantage is provided by embedding in the body of the first seal ring a reinforcement ring, preferably made of metal and with a L-shaped cross section. This ensures a limited and controlled deformation of the first seal ring under action of the external fluid pressure.
  • the cross section of the first seal ring can also have a U-shape, this enabling the seal ring to become wedged in the frustoconical housing, so maintaining an optimal sealing capacity.
  • first seal ring is provided with an annular rib in correspondence with its edge, the external surface of the pin region housing said first seal ring before make-up being provided with a corresponding annular recess or step in order to stably house the rib.
  • the housing for the second seal ring placed internally to the joint, is configured to best match the shape of the second seal ring, and vice versa, whereby the second seal ring works synergistically with its housing both during and after make up.
  • Various cross section shapes for the second seal ring are provided which can be selected in dependence of the external fluid pressure acting on the joint.
  • an improvement in the sealing capacity is achieved without increasing costs since the housing for the second seal ring in the joint according to the invention is easy to make and is not more complex or expensive to produce than the currently used groove configurations, which house standard O-rings of circular cross section.
  • the V-sectioned mouth ensures a better contact of the ring with the surfaces of pin and box when external fluid pressure is exerted on that end even in the annular space comprised between first and second seal rings.
  • the external protruding annular ribs either on one or both of the internal and external surfaces, ensure a better specific pressure on the surfaces of pin and box to which they adhere.
  • the seal ring internal surface ensures a good positioning and contact in the seal ring housing made on the pin external surface.
  • a reinforcement metal ring in the part of the body positioned more internally within the joint ensures that the second seal ring holds tight on the pin, creating a hoop tension.
  • the reinforcement ring is firmly fitted in the V-sectioned mouth and the seal ring is also provided with its own annular rib, in correspondence with an edge of a base, suitable during make-up to engage between the internal surface of the box, underneath a shoulder, and the external surface of the pin in order to further improve sealing.
  • the first seal ring in all its embodiments, is advantageously pre-mounted onto the pin, thus avoiding damage of this seal ring during make-up.
  • the second seal ring in its second and third embodiments it is also pre-mounted on the pin before make-up. Besides, in these cases, the second seal ring provides additional overlapped or redundant sealing functions, which secure tightness of the whole joint, even when one of the functions is itself overcome by the external fluid.
  • the second seal ring is instead pre-mounted in its housing on the internal wall of the box. After completion of make up, the second seal ring, whichever of the embodiments is used, is retained in an annular housing by the inner surface of the box and the outer surface of the pin.
  • This annular housing can also be provided with a finishing and a coating layer.
  • the housing has a geometry especially designed to cooperate with the seal. The joint of the invention needs only limited additional machining operations apart from the common threading operations.
  • a reinforcement ring preferably embedded in the sealing rings in their various shapes, prevents twisting of the ring, renders make up operation easier, and assures easier overall handling and make up of the seal ring itself.
  • a coating can be applied to the surfaces involved by the second seal ring for protecting the machined surface of the pin close to the vanishing thread region of the joint which is likely to be exposed to contact with corrosive external agents.
  • Figure 1 shows a sectional view of the joint projected on an axial plane in accordance with the present invention before make-up with one seal ring pre- mounted
  • Figure 2 shows a sectional view of the joint projected on an axial plane in accordance with the present invention after make up with two seal rings mounted
  • Figure 3 shows a sectional enlarged view of one seal ring of the joint of Fig. 1 in its unloaded position
  • Figure 4 shows a sectional view of a second embodiment of the joint projected on an axial plane in accordance with the present invention with two seal rings mounted
  • Figures 5 and 6 respectively show sectional views of two different embodiments of one seal ring of the joint of Fig. 2 and 4,
  • Figure 7 shows another seal ring of the joint of fig. 4 in an unloaded position
  • Figure 8 shows a sectional view of a third embodiment of the joint projected on an axial plane in accordance with the present invention with two seal rings mounted
  • Figure 9 shows a seal ring of the joint of fig. 8 in an unloaded position.
  • DETAILED DESCRIPTION Throughout the description the surfaces of the different elements of the joint are called external or internal with respect to the joint axis A.
  • a threaded joint connecting two pipes together: a male pipe, commonly called pin 2, with a nominal external diameter D, and a female pipe also called box 3, with a nominal external diameter D1 equal to or greater than D.
  • the pin 2 has an external threaded portion 4 with male threads of appropriate profile, e.g. trapezoidal, the box 3 having an internal threaded portion 5 with female threads of profile complementary to that of the male threads.
  • the common axis of pin 2 and box 3 is indicated by A.
  • the box 3 ends with a nose 15.
  • the joint defines an inner space 16, containing the axis A of pin and box, in which the fluid, for example a hydrocarbon, such as natural gas or petroleum or other similar fluid, flows and an outer space 17 which can be in contact with fluids of various kinds such as sea water in some applications.
  • first seal ring 30 of elastomeric material.
  • the seal ring 30 has a frustoconical shape and its external surface 31 is tapered towards the internal part of the joint 1.
  • the external surface 31 of the seal ring 30 matches the internal surface 32 of the lip 33 of the box 3, which has also a complementary frustoconical shape, for an appropriate length.
  • the seal ring 30 has a reinforcement ring 34 embedded in its body.
  • the reinforcement ring 34 has a cross section, viewed in projection on an axial plane, of L-shape with two arms 35, 36 perpendicular to each other.
  • the angle ⁇ of the L-shape can also be slightly larger or smaller than 90° and alternately the two arms 35, 36 can be of different length depending on the wrapping force that must be exerted on the pin 2, on the magnitude of the external fluid pressure that is exerted in the operative environment of the joint and on the final location that has to be reached by the ring after its initial sliding towards the internal part of the joint under action of the external fluid.
  • the reinforcement ring 34 is positioned as shown in figures 2 and 4, i.e. with the arm 35 parallel to the axis of the seal ring 30 and the arm 36 perpendicu- lar to the axis of said ring 30.
  • the axis of the seal ring 30 is the same common axis A of pin 2 and box 3.
  • Figure 6 shows a second embodiment of the first seal ring 40 having a U-shaped cross section, with the external arm 41 preferably shorter than the internal arm 42.
  • the reinforcement ring 43 embedded in the body of the seal ring 40, has an L- shaped cross section, viewed in projection on an axial plane, with two arms 44, 45 perpendicular to each other.
  • the angle ⁇ of the L-shape can also be slightly larger or smaller than 90° and the two arms 44, 45 can be of different length.
  • the arm 44 is embedded in the external arm 41 of the body of the seal ring 40 parallel to the joint axis A, whereas the arm 45 is embedded in the body of the seal ring 40 perpendicularly to the joint axis A.
  • the reinforcement ring in both embodiments of the first seal ring can be completely embedded in the seal ring or can have one of its surfaces exposed to the exterior of the seal ring, either flush to a base or protruding from this base.
  • the internal surface 37, 47 of the first seal ring 30, 40 has a frus- toconical shape with a very slight taper, of an angle ⁇ lower than 10°.
  • the portion of the box 3 near the end of the thread 5 comprises an annular groove 18 between box nose 15 and the thread end. This groove 18 is the housing for the second seal ring 6.
  • the seal ring 6 has an external surface with two annular ribs 1 1 , 12 separated by an annular furrow 13.
  • the ribs 1 1 , 12 have crests preferably rounded or of any other appropriate shape.
  • the external surface of the second seal ring 6 contacts the bottom of the groove. This bottom is preferably flat in the axial direction in order to make machining easier.
  • the furrow 13 and the ribs 1 1 , 12 have two main advantages:
  • the furrow 13 works as a lung, providing the needed radial deformation to allowing the internal surface of the second seal ring 6 to be squeezed more easily;
  • the ribs 1 1 , 12 generate a load concentration, thus increasing sealing contact and acting as double independent sealing barriers.
  • the seal ring 6 has two bases 8, 9 axially opposite to each other.
  • One or both bases 8, 9 are substantially, but not exclusively, flat.
  • the internal surface of the second seal ring 6 has two frustoconical surfaces or flanks 19, 20 that are V-shaped, when seen in axial section.
  • the taper angle ⁇ of the surfaces 19, 20 can be defined as a function of thread parameters, i.e. taper, stab angle, etc.
  • a preferred value for the angle ⁇ is 45°.
  • each surface 19 and 20 can also have different values ⁇ and ⁇ _ This embodiment is shown in particular in figure 3.
  • the second seal ring 6 has a section with specific dimensions.
  • the thickness "t" of the seal ring 6 in the axial direction is defined by the thread width, the thickness "t" of the ring 6 being larger than the axial length of the void "b" (Fig. 1 ) between two crests of the thread. This facilitates jump over of the crests by the seal ring apex 10 during make up.
  • the depth "d" of the groove 18 of the box 3 in the radial direction is preferably between 3 and 15 mm.
  • the groove 18 should house about 75% of the thickness of the second seal ring 6 in the radial direction, when the latter is in the unloaded position.
  • the taper angles ⁇ and Y of the flanks 19 and 20 are chosen with sizes such that the following relationships with the stab angle ⁇ and load angle ⁇ of the thread flanks are satisfied: ⁇ > ⁇ and Y > ⁇ .
  • the apex 10 of the seal ring 6, where the two tapered frustoconical surfaces 19 and 20 meet, has preferably a rounded shape like a fillet when seen in section.
  • the second seal ring 6 is a simple but effective improvement over conventional O- rings currently used in the field. Main advantages are its frustoconical annular surfaces 19, 20, tapering towards the centre of the seal ring and joined by the apex or fillet 10 therebetween, which facilitate forward or backward movement of the seal ring over the threads, thus avoiding damage.
  • the internal surface of the seal ring 6 also generates a load concentration, thus increasing sealing contact and improving sealability of the seal ring 6 when made up.
  • This seal ring 6 can advantageously have a reinforcement ring 7 of different cross sections embedded in its body.
  • a reinforcement ring 7 of different cross sections embedded in its body With particular reference to figure 4, where the same features of the embodiments described above are indicated by the same reference numerals, there is shown a second embodiment of the joint according to the invention.
  • the first seal ring 30, positioned in an external region of the joint 1 is associated with a second seal ring 21 positioned more internally within the joint.
  • the cross sectional shape of the seal ring 21 is configured to provide several improved sealing functions.
  • the seal ring 21 has a main body on which one or more annular ribs 22 are externally provided separated by annular grooves 22'. At that extremity which is closer to the threaded portions 4, 5 of pin and box, the seal ring 21 has a base 24 substantially, but not necessarily, flat. Close to the base 24 there is provided a reinforcement ring 25, of another material which has greater stiffness, preferably but not exclusively metal.
  • the reinforcement ring 25 can be completely embedded in the seal ring 21 or can have one of its surfaces exposed to the exterior of the seal ring 21 , either flush to the base 24 or protruding from said base 24.
  • the reinforcement ring 25 can ad- vantageously have various cross section shapes.
  • the seal ring 21 has two annular lips 26, 27 which respectively protrude beyond the perimeter of the ring 21 in respective skewed directions with respect to the axis A, when considered in an unloaded position as illustrated in Fig. 7.
  • annular groove is defined, which in axial section appears as a V-shaped mouth 28.
  • the internal surface 23 of the seal ring 21 is undulated in an axial direction and comprises at least one annular rib 29 separated by annular grooves 29', in a section projected on an axial plane.
  • the internal surface 23 of the seal ring 21 is without abrupt variations. In this case it can have a cylindrical shape, or alternately a rounded or toroidal shape or a frustoconical shape with an angle of conicity ⁇ of the surface 23 with reference to the axis A of about 3°. This facilitates mounting of the ring 21 on the pin 2.
  • the seal ring 21 exerts a wrapping force which presses its internal surface against the external pin surface, thus enhancing tightness between seal ring 21 and the external surface of the pin 2.
  • This wrapping force exerted by the seal ring 21 can be further enhanced by the small taper of the surface of the pin 2 in the region designed for the second seal ring 21 after make up is complete.
  • the surface of this region can be inclined to the axis A by an angle ⁇ smaller than 15° preferably 3°. This has the function of pre- venting the seal ring 21 from slipping away from its position during operation by opposing an increased gripping force.
  • This seal ring 60 has a cross section on an axial plane substantially rectangular and provided with a small rib 61 in correspondence with an edge of said cross section.
  • the small rib 61 (Fig. 9) is the section of an annular protuberance protruding in the axial direction.
  • the seal ring 60 can also be provided with a reinforcing ring, for example having a cross section of L-shape, completely embedded in the seal ring or having one of its surfaces exposed to the exterior of the seal ring, either flush to a base or pro- truding from this base.
  • a reinforcing ring for example having a cross section of L-shape, completely embedded in the seal ring or having one of its surfaces exposed to the exterior of the seal ring, either flush to a base or pro- truding from this base.
  • the internal surface of the nose 15 of the box 3 has a cylindrical shape complementary to the shape of the external surface of the seal ring 60.
  • the external surface of the region of the pin 2, where said ring 60 is housed before make-up, has also a cylindrical shape but it is provided with an annular re- cess or step in order to hold the rib 61 in a stable way.
  • the first seal ring is advantageously pre- mounted on the pin 2, thus avoiding damage of this seal ring during make-up.
  • the second seal ring 70 in this third embodiment of the joint, it is also pre-mounted on the pin before make-up.
  • This second seal ring 70 is shown mounted on the joint in an unloaded position in Fig. 9.
  • the cross sectional shape of the seal ring 70 is configured to provide improved sealing functions. It is provided with a base 74 adapted to abut on a shoulder 80 of the box 3.
  • the seal ring 70 has two annular lips 76, 77 which respectively protrude beyond the perimeter of the ring 70 in respective skewed directions with respect to the axis A, when considered in the unloaded position of Fig. 9.
  • annular groove is defined, which in axial section appears as a V- shaped mouth.
  • This annular groove advantageously houses a reinforcement ring 75, firmly fitted in said groove.
  • the ring 75 preferably has a circular cross section and is made of material different from an elastomer but of greater stiffness, preferably but not ex- clusively metal.
  • the seal ring 70 exerts a wrapping force which presses its internal surface against the external pin surface, thus enhancing tightness between seal ring 70 and the external surface of the pin 2.
  • the second seal ring 70 is also provided with its own annular rib 79 in correspondence with an edge of the base 74. This annular rib 79 is able during make-up to engage between the internal surface of the box 3, underneath the shoulder 80, and the external surface of the pin 2 in order to further improve sealing.
  • both external and internal surfaces of the seal ring 70 are without abrupt variations. In this case they can have a cylindrical shape, or alternately a rounded or toroidal shape or a frustoconical shape.
  • the seal ring 70 may have its main body provided externally and/or internally with one or more annular ribs separated by annular grooves, as in the section projected on an axial plane of Fig. 7.
  • the combination of an embodiment of the first or external seal ring 30, 40, 60 with any of the described embodiments of the internal or second seal ring 6, 21 , 70 offers an optimal protection to the joint 1.
  • Both first and second seal rings, which are located at the extremity of the box, combine their individual sealing functions to prevent external fluids which occupy the space 17 external to the joint from leaking into the threaded zone of the joint 1.
  • the seal rings described can be made of elastomeric materials, which in this application is intended to include any natural or synthetic material having elastic properties including rubbers, plastics, polymers, etc.
  • the reinforcement rings, completely or partially embedded or firmly fitted in the body of the seal rings in any of the embodiments illustrated above, are made of various materials, preferably metal, stronger than the elastomeric material of the seal rings.
  • the reinforcement rings can be made of aluminium, cop- per, silver, nickel, steel, or stainless steel. Some reinforcement rings are plated or coated with cadmium, copper, nickel, silver, gold, or indium. Others are heat- treated, age-hardened or annealed.
  • the radial thickness of the reinforcement rings must always be smaller than the radial thickness of the elastomeric seal rings, in order to allow deformation of the elastomer, when compressed in the space between pin and box.
  • a coating is applied to those surfaces of both the pin and box which remain in contact with the first and second seal rings in the various embodiments.
  • the threaded joint of the invention thus offers improved sealability and protection against make up and break-out damage by virtue of the aforementioned features.
  • the joint is to be used preferably in the field of OCTG and line pipe connections for the oil & gas industry, especially in offshore applications. It can be employed at depths up to 3500m, at which the threaded part still remains protected from external water infiltration.
  • the figures 2, 4 and 8 schematically show the joint with the seal rings in a loaded position. Therefore, the shape of the seal rings could be different from that shown, in accordance with the different load conditions.

Abstract

La présente invention concerne un joint fileté (1) comprenant un premier anneau d’étanchéité (30) doté d’une forme conique en coupe dans un plan axial, cet anneau comprenant un anneau de renforcement métallique en forme de L (34) imbriqué dans celui‑ci, et un second anneau d’étanchéité (6) positionné plus à l’intérieur par rapport au premier anneau d’étanchéité (30) et placé dans un logement (18) entre l’extrémité d’une section filetée (5) et le nez (15) de la boîte. Le second anneau d’étanchéité (6) possède une première base, une seconde base à l’opposé dans le plan axial à la première base, et des ailettes annulaires protubérantes sur la surface externe ou sur une surface interne.
PCT/EP2009/052388 2008-02-29 2009-02-27 Joint fileté avec anneau d’étanchéité élastique amélioré WO2009106623A1 (fr)

Priority Applications (8)

Application Number Priority Date Filing Date Title
JP2010548127A JP2011514490A (ja) 2008-02-29 2009-02-27 改良した弾性シールリングを有するねじ結合部
MX2010009517A MX2010009517A (es) 2008-02-29 2009-02-27 Empalme roscado con anillo de sellado flexible mejorado.
CA2716586A CA2716586C (fr) 2008-02-29 2009-02-27 Joint filete avec anneau d'etancheite elastique ameliore
BRPI0907993-9A BRPI0907993B1 (pt) 2008-02-29 2009-02-27 Junta rosqueada
US12/920,085 US8262140B2 (en) 2008-02-29 2009-02-27 Threaded joint with improved resilient seal ring
CN200980106481.1A CN102027186B (zh) 2008-02-29 2009-02-27 具有增强弹性密封环的螺纹接头
RU2010139822/03A RU2472916C2 (ru) 2008-02-29 2009-02-27 Резьбовое соединение с усовершенствованными эластичными уплотнительными кольцами
NO20101182A NO337939B1 (no) 2008-02-29 2010-08-24 Gjenget skjøt med forbedret, fjærende tetningsring

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP08102184A EP2096253B1 (fr) 2008-02-29 2008-02-29 Raccord fileté avec bagues d'étanchéité souples améliorées
EP08102184.2 2008-02-29

Publications (1)

Publication Number Publication Date
WO2009106623A1 true WO2009106623A1 (fr) 2009-09-03

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2009/052388 WO2009106623A1 (fr) 2008-02-29 2009-02-27 Joint fileté avec anneau d’étanchéité élastique amélioré

Country Status (13)

Country Link
US (1) US8262140B2 (fr)
EP (1) EP2096253B1 (fr)
JP (1) JP2011514490A (fr)
CN (1) CN102027186B (fr)
AR (1) AR070553A1 (fr)
AT (1) ATE471433T1 (fr)
BR (1) BRPI0907993B1 (fr)
CA (1) CA2716586C (fr)
DE (1) DE602008001552D1 (fr)
MX (1) MX2010009517A (fr)
NO (1) NO337939B1 (fr)
RU (1) RU2472916C2 (fr)
WO (1) WO2009106623A1 (fr)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8840152B2 (en) 2010-03-26 2014-09-23 Tenaris Connections Limited Thin-walled pipe joint
US9004544B2 (en) 2009-04-22 2015-04-14 Tenaris Connections Limited Threaded joint for tubes, pipes and the like
US9234612B2 (en) 2007-06-22 2016-01-12 Tenaris Connections Limited Threaded joint with energizable seal
RU2573132C2 (ru) * 2010-12-03 2016-01-20 Фридр.Ишебек Гмбх Сцепление, в частности, для соединения анкерных штанг
US9383045B2 (en) 2007-07-16 2016-07-05 Tenaris Connections Limited Threaded joint with resilient seal ring
US9644248B2 (en) 2013-04-08 2017-05-09 Dalmine S.P.A. Heavy wall quenched and tempered seamless steel pipes and related method for manufacturing said steel pipes
US9657365B2 (en) 2013-04-08 2017-05-23 Dalmine S.P.A. High strength medium wall quenched and tempered seamless steel pipes and related method for manufacturing said steel pipes
US9803256B2 (en) 2013-03-14 2017-10-31 Tenaris Coiled Tubes, Llc High performance material for coiled tubing applications and the method of producing the same
KR20170136078A (ko) * 2016-05-30 2017-12-11 주식회사 포스코 유정관용 조인트
US9970242B2 (en) 2013-01-11 2018-05-15 Tenaris Connections B.V. Galling resistant drill pipe tool joint and corresponding drill pipe
US10844669B2 (en) 2009-11-24 2020-11-24 Tenaris Connections B.V. Threaded joint sealed to internal and external pressures
US11105501B2 (en) 2013-06-25 2021-08-31 Tenaris Connections B.V. High-chromium heat-resistant steel
US11124852B2 (en) 2016-08-12 2021-09-21 Tenaris Coiled Tubes, Llc Method and system for manufacturing coiled tubing
US11952648B2 (en) 2011-01-25 2024-04-09 Tenaris Coiled Tubes, Llc Method of forming and heat treating coiled tubing

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE602007011046D1 (de) * 2007-06-27 2011-01-20 Tenaris Connections Ag Gewindeverbindung mit unter Druck setzbarer Dichtung
DE602007008890D1 (de) * 2007-08-24 2010-10-14 Tenaris Connections Ag Verfahren zur Erhöhung der Ermüdungsbeständigkeit einer Schraubverbindung
DE602007013892D1 (de) 2007-08-24 2011-05-26 Tenaris Connections Ag Gewindeverbindungsstück mit hoher Radiallast und unterschiedlich behandelten Oberflächen
DE102010001979A1 (de) * 2009-12-09 2011-06-16 Robert Bosch Gmbh Anordnung und Verfahren zur Abdichtung eines Fügebereichs zwischen einem ersten Fügepartner und einem zweiten Fügepartner
EP2372208B1 (fr) * 2010-03-25 2013-05-29 Tenaris Connections Limited Joint fileté avec bride de joint élastomère
US8424259B2 (en) * 2011-08-03 2013-04-23 Column & Post, Inc. System and method for installing columns
WO2013101852A1 (fr) * 2011-12-27 2013-07-04 Watts John Dawson Raccord de tuyau fileté à couple élevé
CN103982146A (zh) * 2014-06-09 2014-08-13 平顶山市安泰华矿用安全设备制造有限公司 一种水利冲孔用高低压密封钻杆
WO2016119218A1 (fr) * 2015-01-30 2016-08-04 华为技术有限公司 Système, appareil et procédé de synchronisation de configuration de service supplémentaire d'appel
US10434554B2 (en) 2017-01-17 2019-10-08 Forum Us, Inc. Method of manufacturing a coiled tubing string
CA3089510A1 (fr) * 2018-01-29 2019-08-01 BYRNE, Jeanette Joint d'etancheite pour raccord de tuyau flexible
CN109736973B (zh) * 2019-01-30 2022-04-29 北京星际荣耀空间科技股份有限公司 贮箱过渡环及推进剂贮箱
CN113544357A (zh) * 2019-03-20 2021-10-22 美国圣戈班性能塑料公司 密封件
CA3156217A1 (fr) * 2019-10-28 2021-05-06 Byron Raul Lopez Robayo Nouvel accouplement et procede de raccord de tuyaux standardises a.p.i. pour l'extraction de produits petroliers
KR20210111376A (ko) * 2020-03-02 2021-09-13 현대자동차주식회사 수소공급장치 및 이에 사용되는 실링유닛
US11692630B2 (en) * 2020-04-21 2023-07-04 Ford Global Technologies, Llc Redundant seal with radial features
US20230361502A1 (en) * 2022-05-06 2023-11-09 Halliburton Energy Services, Inc. Seal for electrical and pressure isolation

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2276647A (en) * 1993-04-02 1994-10-05 Vetco Gray Inc Abb Casing hanger seal assembly
WO2002068854A1 (fr) * 2001-01-20 2002-09-06 Otten, Gregory, K. Joint anticorrosion remplaçable pour connexions filetees
WO2002086369A1 (fr) * 2001-04-25 2002-10-31 G.B. Tubulars, Inc. Manchon taraude ameliore equipe d'un systeme d'etancheite par epanchement
FR2848282A1 (fr) * 2002-12-09 2004-06-11 Vallourec Mannesmann Oil & Gas Procede de realisation d'un joint filete tubulaire etanche vis-a-vis de l'exterieur

Family Cites Families (113)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1671458A (en) 1925-05-19 1928-05-29 Guiberson Corp Rod joint
US1999706A (en) * 1934-01-25 1935-04-30 Ferdinand J Spang Coupling
US2075427A (en) 1936-12-28 1937-03-30 W L Pearce Pipe joint
US2211173A (en) 1938-06-06 1940-08-13 Ernest J Shaffer Pipe coupling
US2487241A (en) 1947-01-16 1949-11-08 Lewis D Hilton Thread seal and buffer gasket for pipe couplings
US2631871A (en) 1949-04-30 1953-03-17 Albert L Stone Pressure responsive pipe joint seal
US3054628A (en) 1954-06-08 1962-09-18 Atlas Bradford Company Pipe coupling having a teflon sealing gasket
FR1149513A (fr) 1955-07-25 1957-12-27 Joint élastique pour tuyaux
US2992613A (en) 1960-08-30 1961-07-18 Albert G Bodine Sonic well pump tubing string
US3307860A (en) 1965-01-15 1967-03-07 Mobil Oil Corp Joint for liner-carrying well pipe
FR1489013A (fr) 1965-11-05 1967-07-21 Vallourec Joint d'assemblage pour tubes métalliques
US3572777A (en) 1969-05-05 1971-03-30 Armco Steel Corp Multiple seal, double shoulder joint for tubular products
DE2131318C3 (de) 1971-06-24 1973-12-06 Fried. Krupp Huettenwerke Ag, 4630 Bochum Verfahren zum Herstellen eines Beweh rungs Stabstahles für Spannbeton
FR2190237A5 (fr) 1972-06-16 1974-01-25 Vallourec
FR2190238A5 (fr) 1972-06-16 1974-01-25 Vallourec
GB1473389A (en) 1973-05-09 1977-05-11 Dexploitation Des Brevets Ocla Pipe couplings
NO140752C (no) 1977-08-29 1979-11-07 Rieber & Son As Kombinert forme- og tetningselement til bruk i en muffeende i termoplastroer
FR2468823A1 (fr) 1979-10-30 1981-05-08 Vallourec Joint pour tubes destine a l'industrie petroliere
CA1148193A (fr) 1980-01-11 1983-06-14 Kornelis N. Zijlstra Raccord de sections de train de forage, et section de train
US5348350A (en) 1980-01-19 1994-09-20 Ipsco Enterprises Inc. Pipe coupling
US4384737A (en) 1980-04-25 1983-05-24 Republic Steel Corporation Threaded joint for well casing and tubing
US4406561A (en) 1981-09-02 1983-09-27 Nss Industries Sucker rod assembly
US4706997A (en) 1982-05-19 1987-11-17 Carstensen Kenneth J Coupling for tubing or casing and method of assembly
US4508375A (en) 1982-09-20 1985-04-02 Lone Star Steel Company Tubular connection
US4662659A (en) 1983-01-17 1987-05-05 Hydril Company Tubular joint with trapped mid-joint metal-to-metal seal having unequal tapers
US4570982A (en) 1983-01-17 1986-02-18 Hydril Company Tubular joint with trapped mid-joint metal-to-metal seal
DE3310226C2 (de) 1983-03-22 1985-08-22 Friedrichsfeld Gmbh, Steinzeug- Und Kunststoffwerke, 6800 Mannheim Rohrteil oder Fitting
DK162684A (da) 1983-03-22 1984-11-02 Friedrichsfeld Gmbh Roerdel eller fitting
US4475839A (en) 1983-04-07 1984-10-09 Park-Ohio Industries, Inc. Sucker rod fitting
DE3322134A1 (de) 1983-06-20 1984-12-20 WOCO Franz-Josef Wolf & Co, 6483 Bad Soden-Salmünster Zylindrischer dichtungsring
US4591195A (en) 1983-07-26 1986-05-27 J. B. N. Morris Pipe joint
US4602807A (en) 1984-05-04 1986-07-29 Rudy Bowers Rod coupling for oil well sucker rods and the like
JPS616488A (ja) 1984-06-20 1986-01-13 日本鋼管株式会社 油井管用ネジ継手
US4688832A (en) 1984-08-13 1987-08-25 Hydril Company Well pipe joint
US4762344A (en) 1985-01-30 1988-08-09 Lee E. Perkins Well casing connection
US4988127A (en) 1985-04-24 1991-01-29 Cartensen Kenneth J Threaded tubing and casing joint
IT1199343B (it) 1986-12-23 1988-12-30 Dalmine Spa Giunto perfezionato per tubi di rivestimento di pozzi
US4844517A (en) 1987-06-02 1989-07-04 Sierracin Corporation Tube coupling
US4955645A (en) 1987-09-16 1990-09-11 Tuboscope, Inc. Gauging device and method for coupling threaded, tubular articles and a coupling assembly
US4867489A (en) 1987-09-21 1989-09-19 Parker Hannifin Corporation Tube fitting
US4856828A (en) 1987-12-08 1989-08-15 Tuboscope Inc. Coupling assembly for tubular articles
SU1560874A1 (ru) * 1988-03-09 1990-04-30 Ивано-Франковский Институт Нефти И Газа Трубное резьбовое соединение
DE3815455C2 (de) 1988-05-06 1994-10-20 Freudenberg Carl Fa Aufblasbare Dichtung
IT1224745B (it) 1988-10-03 1990-10-18 Dalmine Spa Giunto a tenuta ermetica metallica per tubi
CA1314864C (fr) 1989-04-14 1993-03-23 Computalog Gearhart Ltd. Configuration de joint a compression et de controle de pression pour outils de fond de trou
US6070912A (en) 1989-08-01 2000-06-06 Reflange, Inc. Dual seal and connection
JP3135911B2 (ja) * 1990-10-20 2001-02-19 大豊工業株式会社 金属ガスケットの製造方法
US5137310A (en) 1990-11-27 1992-08-11 Vallourec Industries Assembly arrangement using frustoconical screwthreads for tubes
US5521707A (en) 1991-08-21 1996-05-28 Apeiron, Inc. Laser scanning method and apparatus for rapid precision measurement of thread form
JPH0547619U (ja) * 1991-12-03 1993-06-25 株式会社荒井製作所 密封装置
US5180008A (en) 1991-12-18 1993-01-19 Fmc Corporation Wellhead seal for wide temperature and pressure ranges
NO941302L (no) 1993-04-14 1994-10-17 Fmc Corp Pakning for rör med stor diameter
US5505502A (en) * 1993-06-09 1996-04-09 Shell Oil Company Multiple-seal underwater pipe-riser connector
JP2599911Y2 (ja) * 1993-12-22 1999-09-27 坂本工業株式会社 車両用オイルタンクとオイルポンプとの接続部のシール構造
US5515707A (en) 1994-07-15 1996-05-14 Precision Tube Technology, Inc. Method of increasing the fatigue life and/or reducing stress concentration cracking of coiled metal tubing
DE69625472T2 (de) 1995-03-23 2003-09-25 Hydril Co Schraubrohrverbindung
CN2232070Y (zh) * 1995-07-07 1996-07-31 柳发明 螺纹键插式钻杆接头
US5810401A (en) 1996-05-07 1998-09-22 Frank's Casing Crew And Rental Tools, Inc. Threaded tool joint with dual mating shoulders
FR2761450B1 (fr) * 1997-03-27 1999-05-07 Vallourec Mannesmann Oil & Gas Joint filete pour tubes
UA71575C2 (uk) 1998-09-07 2004-12-15 Валлурек Маннесманн Ойл Енд Гес Франс Різьбове з'єднання двох металевих труб з великим моментом загвинчування
UA66876C2 (uk) 1998-09-07 2004-06-15 Валлурек Маннесманн Ойл Енд Гес Франс Різьбове з'єднання двох металевих труб з пазом, виконаним в різьбі
US6299705B1 (en) 1998-09-25 2001-10-09 Mitsubishi Heavy Industries, Ltd. High-strength heat-resistant steel and process for producing high-strength heat-resistant steel
FR2784446B1 (fr) 1998-10-13 2000-12-08 Vallourec Mannesmann Oil & Gas Assemblage filete integral de deux tubes metalliques
US6173968B1 (en) 1999-04-27 2001-01-16 Trw Inc. Sealing ring assembly
JP3083517B1 (ja) 1999-06-28 2000-09-04 東尾メック株式会社 管継手
CN1178015C (zh) 1999-09-16 2004-12-01 西德尔卡有限公司 高安定性及稳定性的螺纹接头
AR020495A1 (es) 1999-09-21 2002-05-15 Siderca Sa Ind & Com Union roscada de alta resistencia al sobretorque y compresion
US6764108B2 (en) 1999-12-03 2004-07-20 Siderca S.A.I.C. Assembly of hollow torque transmitting sucker rods
US6991267B2 (en) 1999-12-03 2006-01-31 Siderca S.A.I.C. Assembly of hollow torque transmitting sucker rods and sealing nipple with improved seal and fluid flow
FR2807095B1 (fr) 2000-03-31 2002-08-30 Vallourec Mannesmann Oil & Gas Element filete tubulaire delarde pour joint filete tubulaire resistant a la fatigue et joint filete tubulaire resultant
US6447025B1 (en) 2000-05-12 2002-09-10 Grant Prideco, L.P. Oilfield tubular connection
EP1296088A4 (fr) 2000-06-07 2003-07-09 Sumitomo Metal Ind Liaison a filetage conique
IT1318179B1 (it) 2000-07-17 2003-07-23 Dalmine Spa Giunzione filettata integrale per tubi.
IT1318753B1 (it) 2000-08-09 2003-09-10 Dalmine Spa Giunzione filettata integrale a profilo continuo pr tubi
US7108063B2 (en) 2000-09-25 2006-09-19 Carstensen Kenneth J Connectable rod system for driving downhole pumps for oil field installations
US6857668B2 (en) * 2000-10-04 2005-02-22 Grant Prideco, L.P. Replaceable corrosion seal for threaded connections
US6494499B1 (en) 2000-10-31 2002-12-17 The Technologies Alliance, Inc. Threaded connector for pipe
DE10108476A1 (de) * 2001-02-22 2002-09-12 Celanese Chem Europe Gmbh Verfahren zur Herstellung von Aldehyden
JP2002323179A (ja) * 2001-04-24 2002-11-08 Sekisui Chem Co Ltd 管継手
JP2003096534A (ja) 2001-07-19 2003-04-03 Mitsubishi Heavy Ind Ltd 高強度耐熱鋼、高強度耐熱鋼の製造方法、及び高強度耐熱管部材の製造方法
JP4313962B2 (ja) * 2001-07-25 2009-08-12 株式会社オンダ製作所 継手
US6755447B2 (en) 2001-08-24 2004-06-29 The Technologies Alliance, Inc. Production riser connector
US6682101B2 (en) 2002-03-06 2004-01-27 Beverly Watts Ramos Wedgethread pipe connection
ITRM20020234A1 (it) 2002-04-30 2003-10-30 Tenaris Connections Bv Giunzione filettata per tubi.
GB2388169A (en) 2002-05-01 2003-11-05 2H Offshore Engineering Ltd Pipe joint
US6666274B2 (en) 2002-05-15 2003-12-23 Sunstone Corporation Tubing containing electrical wiring insert
ITRM20020274A1 (it) 2002-05-16 2003-11-17 Tenaris Connections Bv Giunzione filettata per tubi.
KR100619509B1 (ko) * 2002-06-28 2006-09-08 도요다 지도샤 가부시끼가이샤 연료 전지
FR2844023B1 (fr) 2002-08-29 2005-05-06 Vallourec Mannesmann Oil & Gas Joint filete tubulaire etanche vis-a-vis du milieu exterieur
ITRM20020445A1 (it) 2002-09-06 2004-03-07 Tenaris Connections Bv Giunzione filettata per tubi.
US7074286B2 (en) 2002-12-18 2006-07-11 Ut-Battelle, Llc Wrought Cr—W—V bainitic/ferritic steel compositions
US6817633B2 (en) 2002-12-20 2004-11-16 Lone Star Steel Company Tubular members and threaded connections for casing drilling and method
ITRM20030065A1 (it) 2003-02-13 2004-08-14 Tenaris Connections Bv Giunzione filettata per tubi.
US7431347B2 (en) 2003-09-24 2008-10-07 Siderca S.A.I.C. Hollow sucker rod connection with second torque shoulder
US20050093250A1 (en) 2003-11-05 2005-05-05 Santi Nestor J. High-strength sealed connection for expandable tubulars
JP5171041B2 (ja) 2004-02-02 2013-03-27 テナリス・コネクシヨンズ・アクチエンゲゼルシヤフト 筒状部材のためのねじ用保護器
JP2005221038A (ja) 2004-02-06 2005-08-18 Sumitomo Metal Ind Ltd 油井管用ネジ継手、及びその製造方法
JP2006210843A (ja) * 2005-01-31 2006-08-10 Fujitsu Ltd 可変キャパシタ及びその製造方法
ITRM20050069A1 (it) 2005-02-17 2006-08-18 Tenaris Connections Ag Giunzione filettata per tubi provvista di tenuta.
US20060214421A1 (en) 2005-03-22 2006-09-28 Intelliserv Fatigue Resistant Rotary Shouldered Connection and Method
US7478842B2 (en) 2005-05-18 2009-01-20 Hydril Llc Coupled connection with an externally supported pin nose seal
AR058961A1 (es) 2006-01-10 2008-03-05 Siderca Sa Ind & Com Conexion para varilla de bombeo con mayor resistencia a l afatiga obtenida aplicando interferencia diametral para reducir la interferencia axial
RU65104U1 (ru) * 2007-03-22 2007-07-27 Открытое акционерное общество "Татнефть" им. В.Д. Шашина Соединение профильных труб перекрывателей скважин
AR061224A1 (es) 2007-06-05 2008-08-13 Tenaris Connections Ag Una union roscada de alta resistencia, preferentemente para tubos con recubrimiento interno.
EP2006589B1 (fr) 2007-06-22 2011-08-31 Tenaris Connections Aktiengesellschaft Joint fileté avec étanchéité énergisable
DE602007011046D1 (de) 2007-06-27 2011-01-20 Tenaris Connections Ag Gewindeverbindung mit unter Druck setzbarer Dichtung
EP2017507B1 (fr) 2007-07-16 2016-06-01 Tenaris Connections Limited Joint fileté avec bague d'étanchéité souple
DE602007013892D1 (de) 2007-08-24 2011-05-26 Tenaris Connections Ag Gewindeverbindungsstück mit hoher Radiallast und unterschiedlich behandelten Oberflächen
DE602007008890D1 (de) 2007-08-24 2010-10-14 Tenaris Connections Ag Verfahren zur Erhöhung der Ermüdungsbeständigkeit einer Schraubverbindung
EP2243920A1 (fr) 2009-04-22 2010-10-27 Tenaris Connections Aktiengesellschaft Joint fileté pour tubes, tuyaux et similaires
EP2325435B2 (fr) 2009-11-24 2020-09-30 Tenaris Connections B.V. Joint fileté étanche à des pressions internes et externes [extrêmement hautes]
EP2372208B1 (fr) 2010-03-25 2013-05-29 Tenaris Connections Limited Joint fileté avec bride de joint élastomère
EP2372211B1 (fr) 2010-03-26 2015-06-03 Tenaris Connections Ltd. Raccord de tuyau à paroi mince et méthode pour coupler un premier tuyau à un second tuyau

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2276647A (en) * 1993-04-02 1994-10-05 Vetco Gray Inc Abb Casing hanger seal assembly
WO2002068854A1 (fr) * 2001-01-20 2002-09-06 Otten, Gregory, K. Joint anticorrosion remplaçable pour connexions filetees
WO2002086369A1 (fr) * 2001-04-25 2002-10-31 G.B. Tubulars, Inc. Manchon taraude ameliore equipe d'un systeme d'etancheite par epanchement
FR2848282A1 (fr) * 2002-12-09 2004-06-11 Vallourec Mannesmann Oil & Gas Procede de realisation d'un joint filete tubulaire etanche vis-a-vis de l'exterieur

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9234612B2 (en) 2007-06-22 2016-01-12 Tenaris Connections Limited Threaded joint with energizable seal
US9383045B2 (en) 2007-07-16 2016-07-05 Tenaris Connections Limited Threaded joint with resilient seal ring
US9004544B2 (en) 2009-04-22 2015-04-14 Tenaris Connections Limited Threaded joint for tubes, pipes and the like
US10844669B2 (en) 2009-11-24 2020-11-24 Tenaris Connections B.V. Threaded joint sealed to internal and external pressures
US8840152B2 (en) 2010-03-26 2014-09-23 Tenaris Connections Limited Thin-walled pipe joint
RU2573132C2 (ru) * 2010-12-03 2016-01-20 Фридр.Ишебек Гмбх Сцепление, в частности, для соединения анкерных штанг
US11952648B2 (en) 2011-01-25 2024-04-09 Tenaris Coiled Tubes, Llc Method of forming and heat treating coiled tubing
US9970242B2 (en) 2013-01-11 2018-05-15 Tenaris Connections B.V. Galling resistant drill pipe tool joint and corresponding drill pipe
US10378075B2 (en) 2013-03-14 2019-08-13 Tenaris Coiled Tubes, Llc High performance material for coiled tubing applications and the method of producing the same
US9803256B2 (en) 2013-03-14 2017-10-31 Tenaris Coiled Tubes, Llc High performance material for coiled tubing applications and the method of producing the same
US10378074B2 (en) 2013-03-14 2019-08-13 Tenaris Coiled Tubes, Llc High performance material for coiled tubing applications and the method of producing the same
US11377704B2 (en) 2013-03-14 2022-07-05 Tenaris Coiled Tubes, Llc High performance material for coiled tubing applications and the method of producing the same
US9657365B2 (en) 2013-04-08 2017-05-23 Dalmine S.P.A. High strength medium wall quenched and tempered seamless steel pipes and related method for manufacturing said steel pipes
US9644248B2 (en) 2013-04-08 2017-05-09 Dalmine S.P.A. Heavy wall quenched and tempered seamless steel pipes and related method for manufacturing said steel pipes
US11105501B2 (en) 2013-06-25 2021-08-31 Tenaris Connections B.V. High-chromium heat-resistant steel
KR20170136078A (ko) * 2016-05-30 2017-12-11 주식회사 포스코 유정관용 조인트
KR102372616B1 (ko) * 2016-05-30 2022-03-11 주식회사 포스코 유정관용 조인트
US11124852B2 (en) 2016-08-12 2021-09-21 Tenaris Coiled Tubes, Llc Method and system for manufacturing coiled tubing

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RU2472916C2 (ru) 2013-01-20
NO20101182L (no) 2010-11-23
US20110008101A1 (en) 2011-01-13
CA2716586C (fr) 2014-02-11
BRPI0907993B1 (pt) 2019-03-19
RU2010139822A (ru) 2012-04-10
NO337939B1 (no) 2016-07-11
MX2010009517A (es) 2010-12-20
EP2096253B1 (fr) 2010-06-16
ATE471433T1 (de) 2010-07-15
DE602008001552D1 (de) 2010-07-29
CN102027186A (zh) 2011-04-20
CA2716586A1 (fr) 2009-09-03
JP2011514490A (ja) 2011-05-06
US8262140B2 (en) 2012-09-11
AR070553A1 (es) 2010-04-21
CN102027186B (zh) 2014-03-05
BRPI0907993A2 (pt) 2016-06-07
EP2096253A1 (fr) 2009-09-02

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